JP2012188934A - Valve device for compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a valve device for a compressor to reduce noise due to pressure pulsation and suppress a reduction in the efficiency of the compressor; and to ensure the durability to suppress degradation of the performance of the compressor.SOLUTION: In a valve device for a reed valve structure, including: a communication hole 103a or 103b open in a valve plate 103; a valve seat 103e formed at the outer peripheral edge of the communication hole 103a or 103b so as to protrude in a boss-like shape relative to a groove 103f formed outside and around the outer peripheral edge; and a valve body 151 having a base end section 151A connected to the valve plate 103 and also having a front end section 151B capable of making contact with and separating from the seating surface of the valve seat 103e, the valve device is provided with a plurality of (in the figure, three) ribs 103g extending in the radial direction from the peripheral wall of the portion of the valve seat 103e, on which the front end side of the valve body 151 is seated, to the outer peripheral wall of the groove 103f.

Description

  The present invention relates to a valve device that is opened and closed to suck or discharge refrigerant in a compressor used in a refrigeration cycle air conditioner or the like.

  In this kind of compressor, as shown in Patent Document 1, etc., a valve plate interposed between a cylinder head and a cylinder bore is provided with a suction valve that opens and closes a suction hole for sucking refrigerant from the suction chamber into the cylinder bore, and A discharge hole for discharging the refrigerant compressed from the cylinder bore into the discharge chamber is opened, and a suction valve and a discharge valve having a reed valve structure for opening and closing the suction hole and the discharge hole are mounted.

  A valve seat is formed on the outer peripheral edge of each of the suction hole and the discharge hole so as to protrude in a boss shape with respect to a groove formed on the outer periphery thereof.

JP 11-210626 A

  Here, oil mixed in the refrigerant adheres between the valve body and the seating surface of the valve seat, and the valve body comes into close contact with the seating surface, making it difficult to open the valve. When the valve seat has a large radial width (hereinafter simply referred to as “width”) and a large seating area, the close contact force of the valve body with the seating surface increases, and the suction negative pressure or discharge from the cylinder bore when the valve is opened. When the pressure increases and exceeds the contact force (valve opening pressure), the valve opens at once, and the noise increases due to the pressure pulsation (suction pulsation or discharge pulsation) generated at this time, and the efficiency of the compressor decreases. To do.

  In order to solve the above problem, if the seating area is reduced by narrowing the seating surface of the valve body, the seating of the valve body on the valve seat before the noise and efficiency reduction due to pressure pulsation are sufficiently suppressed. Due to the impact at the time, the seat portion on the front end side of the valve body where the impact is large causes damage such as collapse, buckling or fatigue of the valve seat, and deterioration of the compressor performance is promoted due to a decrease in sealing performance.

  The present invention has been made by paying attention to such conventional problems, and suppresses the close contact of the valve body with the seating surface, thereby suppressing noise, maintaining good compressor efficiency, and ensuring durability. Then, it aims at providing the valve apparatus of the compressor which can suppress deterioration of compressor performance.

For this reason, the present invention
A valve plate that is opened and closed to suck or discharge refrigerant and has a valve hole, and is formed on the outer peripheral edge of the valve hole of the valve plate so as to protrude into a boss shape with respect to a groove formed on the outer periphery of the valve plate. A valve device having a reed valve structure including a valve seat, a base end portion connected to the valve plate, and a distal end portion freely contacting and separating from a seating surface of the valve seat;
The shape of the valve seat or a peripheral portion including the valve seat is formed such that a portion corresponding to the distal end side of the valve body is reinforced with respect to a portion corresponding to the proximal end side of the valve body. And

  In a valve device with a reed valve structure, when the valve element is seated, the part of the valve seat where the valve element tip side is seated has a larger stroke when opening and closing the valve than the part where the valve element base end side is seated. A large compressive load acts due to the impact of.

  In this way, the strength of the portion of the valve seat on which the compressive load acts greatly seats on the front end side of the valve body is formed in a shape that is greater than the strength of the portion of the valve body on which the compressive load acts relatively on the base end side. By doing so, collapse, buckling, and fatigue of the valve seat are suppressed, and as a result, deterioration of the compressor performance due to a decrease in sealing performance can be suppressed.

  On the other hand, with such a partial reinforcing structure, at least the portion where the distal end side of the valve body where a relatively small load acts is seated can be reduced to the extent that the required strength can be secured. , The pressure pulsation can be suppressed when the valve is opened, noise can be suppressed, and the efficiency of the compressor can be maintained well.

The longitudinal section showing the variable capacity compressor which provided the valve device concerning the present invention. The perspective view and top view which show the valve apparatus which concerns on 1st Embodiment. The top view which shows the valve apparatus which concerns on 2nd Embodiment. The top view which shows the valve apparatus which concerns on 3rd Embodiment. The top view which shows the valve apparatus which concerns on 4th Embodiment. The top view and longitudinal cross-sectional view which show the valve apparatus which concerns on 5th Embodiment. The top view which shows the valve apparatus which concerns on 6th Embodiment. The partially broken perspective view which shows the valve apparatus which concerns on 7th Embodiment. The top view which shows the valve apparatus which concerns on 8th Embodiment. The figure explaining the subject in the conventional valve apparatus. The figure explaining the suppression effect | action of the collapse of the valve apparatus which concerns on this invention. The figure explaining the buckling and the fatigue | exhaustion suppression effect of the valve apparatus which concern on this invention. The figure which shows distribution of the collapse amount of the valve seat in the conventional valve apparatus.

Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.
FIG. 1 shows a compressor according to an embodiment, and this compressor is a swash plate type variable capacity reciprocating compressor 100 used in a vehicle air conditioner system.

  The compressor 100 includes a cylinder block 101, a front housing 102 connected to one end of the cylinder block 101, and a cylinder head 104 connected to the other end of the cylinder block 101 via a valve plate 103.

  A crank chamber 105 is defined by the cylinder block 101 and the front housing 102, and the drive shaft 106 has radial and thrust bearings 113 with respect to the cylinder block 101 and the front housing 102 so as to cross the crank chamber 105. , 115 and 116 are rotatably supported.

  The front end portion of the drive shaft 106 penetrates through the boss portion 102a of the front housing 102 and protrudes to the outside of the front housing 102. A drive source such as a vehicle engine or motor is connected to the front end portion protruding outside the power transmission device. It is connected via.

A shaft seal device 112 is provided between the drive shaft 106 and the boss portion 102a to block the inside of the front housing 102 (crank chamber 105) from the outside.
In the crank chamber 105, a rotor 108 is fixed to the drive shaft 106, and a swash plate 107 is attached to the rotor 108 via a connecting portion 109.

  The swash plate 107 is supported so that the drive shaft 106 passes through a through-hole formed in the center of the swash plate 107, rotates integrally with the drive shaft 106, and is slidable and tiltable in the axial direction of the drive shaft 106. . Further, the rotor 108 is rotatably supported by a thrust bearing 114 disposed on the front end side inner wall of the front housing 102.

  Between the rotor 108 and the swash plate 107, a coil spring 110 that urges the swash plate 107 in a direction to reduce the inclination angle of the swash plate 107 is mounted, and between the cylinder block 101 and the swash plate 107. Is mounted with a coil spring 111 for urging the swash plate 107 in a direction to increase the inclination angle of the swash plate 107.

  A plurality of cylinder bores 101 a are formed in the cylinder block 101 so as to surround the drive shaft 106, and a piston 117 is accommodated in each cylinder bore 101 a so as to be capable of reciprocating in the axial direction of the drive shaft 106. Each piston 117 is engaged with the outer peripheral portion of the swash plate 107 via a shoe 118. When the swash plate 107 rotates together with the drive shaft 106, each piston 117 reciprocates in the cylinder bore 101a.

  The cylinder head 104 is provided with a suction chamber 119 on an extension line of the drive shaft 106 and a discharge chamber 120 that surrounds the suction chamber 119 in an annular shape. The suction chamber 119 communicates with the cylinder bore 101a via a valve hole 103a provided in the valve plate 103 and a valve body 151a of the suction valve, and the discharge chamber 120 is provided with a valve hole provided in the valve body 151b of the discharge valve and the valve plate 103. It communicates with the cylinder bore 101a via 103b.

  The front housing 102, the cylinder block 101, the valve plate 103, and the cylinder head 104 are fastened by a plurality of through bolts 140 via a gasket (not shown) to form a compressor housing.

  A muffler 121 is provided outside the cylinder block 101. In the muffler 121, a communication passage 121a communicating with the discharge chamber 120 is formed by overlapping with a communication passage 103c formed in the valve plate, and a check valve 200 is incorporated. The check valve 200 is opened only when the pressure in the upstream discharge chamber 120 is higher than the downstream pressure by a predetermined amount or more, and the refrigerant flowing from the discharge chamber 120 through the communication passages 103c and 121a is discharged from the discharge port 121b. It is designed to be discharged.

  The cylinder head 104 is formed with a suction port 104a connected to a suction side refrigerant circuit (evaporator) of the vehicle air conditioner system, and an opening adjusting valve 250 is interposed in the vicinity of the downstream side of the suction port 104a. The refrigerant whose flow rate is adjusted from the side refrigerant circuit (evaporator) through the suction port 104 a and the opening degree adjustment valve 250 is sucked into the suction chamber 119.

A capacity control valve 300 is attached to the cylinder head 104.
The capacity control valve 300 adjusts the opening degree of the communication passage 125 that communicates the discharge chamber 120 and the crank chamber 105, and controls the amount of refrigerant discharged into the crank chamber 105.

  In addition, the refrigerant in the crank chamber 105 passes through the gaps between the bearings 115 and 116 and the drive shaft 106 and enters the suction chamber 119 via the space 127 formed in the cylinder block 101 and the orifice 103 d formed in the valve plate 103. Inflow.

  Therefore, the displacement control valve 300 adjusts the amount of refrigerant introduced into the crank chamber 105 to change the pressure of the crank chamber 105, and the inclination angle of the swash plate 107, that is, the stroke amount of the piston 117 is changed. The discharge capacity of the machine 100 can be controlled.

  The capacity control valve 300 adjusts the energization amount to the built-in solenoid based on the external signal, and the pressure of the suction chamber 119 introduced into the pressure sensing chamber of the capacity control valve 300 via the communication path 126 is a predetermined value. The discharge capacity of the compressor 100 is controlled so that the communication path 125 is forcibly opened by shutting off the power supply to the built-in solenoid, and the discharge capacity of the compressor 100 is controlled to the minimum.

Next, the valve device configured to include the valve body 151a and the valve hole 103a of the suction valve and the valve body 151b and the valve hole 103b of the discharge valve will be described in detail.
First, the basic configuration (conventional configuration) of this type of valve device and the effect on the valve seat due to the compressive load applied to the seating surface of the valve seat by opening and closing the valve body will be described.

  As shown in FIG. 10A, a valve seat 503 is formed on the outer peripheral edge of the valve hole 501 formed in the valve plate 500 so as to protrude in a boss shape with respect to a groove 502 formed on the outer periphery thereof. Yes. By providing the groove 502 to form the boss-shaped valve seat 503, the seating surface of the valve body 600 can be formed with high accuracy, and by pressing the plate-shaped valve plate 500, the valve seat 503 is simultaneously formed with the groove 502. Can be easily processed.

  The valve body 600 composed of an elongated reed valve has a base end portion 601 fixed to the valve plate, and a circular distal end portion 602 that contacts and separates from the top surface (seat surface) of the valve seat 502, thereby opening the valve hole 501. It is configured to open and close.

  As described above, the portion of the valve seat 503 where the front end side of the valve body 600 is seated has a larger stroke amount when the valve is opened and closed compared to the portion where the base end side of the valve body 600 is seated. A large compressive load acts due to the impact of.

  Therefore, when the radial width of the valve seat 503 is reduced in order to reduce the adhesion force of the valve body 600 to the valve seat 503, the strength and noise reduction due to pressure pulsation are sufficiently suppressed before the strength is reduced. Due to the shortage, damage is caused by the compressive load from the portion where the front end side of the valve body 503 is seated.

  As shown in FIGS. 10 (B) and 10 (C), one of the damage forms is that a large compressive load is applied to the seating surface due to the impact when the valve seat is seated, and a large surface pressure (pressure per unit area) is generated. It is “collapse” due to plastic deformation.

  The other is that, as shown in FIGS. 10D, 10E, and 10F, when a compressive load is applied to the seating surface of the valve seat, a bending moment is generated and the buckling load is reached. "Buckling" caused by In addition, there is “fatigue” caused by repeatedly generating a bending moment even when the buckling load is not reached.

  Therefore, in the embodiment described below, in order to avoid damage such as “crush”, “buckling”, and “fatigue”, the shape of the valve seat or the peripheral portion including the valve seat is the tip of the valve body. The part corresponding to the side is formed in a shape reinforced more than the part corresponding to the base end side.

  In the embodiment shown in FIGS. 2A and 2B, a plurality of ribs 103g extending in the radial direction from the peripheral wall of the seated portion of the valve body 151 of the valve seat 103e to the outer peripheral wall of the groove 103f (see FIG. 3).

  The shape of the rib 103g is not only a shape that tapers radially outward as shown in FIGS. 2A and 2B, but also a shape having the same radial width as shown in FIG. 3, as shown in FIG. An arbitrary shape such as a thin shape in the central portion in the radial direction can be used.

  The height of the rib 103g (the height with respect to the bottom of the groove 103f, hereinafter the same) is set to the same height as the seating surface (= valve plate surface) of the valve seat 103e or slightly lower than this. Is done.

The operation of the valve device embodiment will be described.
First, the case where the height of the rib 103g is set to the same height as the seating surface (= valve plate surface) of the valve seat 103e will be described.

  In this case, the peripheral edge of the valve body 151 (151a or 151b) on the tip side is seated on the flat top surface of each rib 103g together with the seating surface of the valve seat 103e. Therefore, since the area of the seating surface including the rib 103g forming portion and the surrounding valve seat 103e is increased, even when a large compression load is received due to the impact when the valve body 151 is seated, the surface pressure is reduced. By the reduction, the collapse can be effectively suppressed (see the model diagram and FIG. 11).

  At the same time, the cross-sectional area of the portion where the rib 103g and the valve seat 103e are integrated (the cross-sectional area in the direction parallel to the valve plate; hereinafter the same) increases and the slenderness ratio λ decreases, so that the buckling of this portion is reduced. The load increases. Thereby, even when a large compressive load is received due to an impact when the front end side of the valve body 151 is seated, buckling can be effectively suppressed, and fatigue due to repeated compressive load can also be effectively suppressed (model FIG. 12 ( B)).

Thus, by suppressing damage such as crushing, buckling, and fatigue of the valve seat 103e, it is possible to suppress deterioration of the compressor performance due to a decrease in sealing performance.
On the other hand, the partial reinforcement of the valve seat 103e increases the effect of suppressing crushing, buckling, and fatigue. As a result, the entire circumference of the valve seat 103e can be narrowed to reduce the total area of the seating surface. As a result, the contact force of the valve body 151 due to oil mixed between the valve body 151 and the seating surface of the valve seat 103e can be reduced, pressure pulsation generated when the valve is opened can be sufficiently suppressed, and noise can be suppressed. The compressor efficiency can be maintained well.

2 (A) and 2 (B), the rib 103g is arranged at one place where the tip of the valve body 151 of the valve seat 103e is seated and at two places on the left seating part in the figure. is doing.
This corresponds to the case in which the amount of collapse of the annular valve seat when the rib is not provided is obtained as shown in FIG. This is because the amount of crushing is larger on the left side of the drawing in the direction connecting the part and the tip part, and the compressive load is considered to act greatly. For example, when the central axis of the cylinder bore 101a is on the left side in FIG. 13 in the direction connecting the proximal end portion 151A and the distal end portion 151B of the valve body 151, generally, the suction force from the cylinder bore is more strongly generated on the left side and the valve seat The compressive load acting on the seating surface increases.

  On the other hand, as shown in FIG. 13, the range of 90 degrees on both sides from the center of the valve seat 103e toward the valve body tip direction is particularly large for the region exceeding 90 degrees, so It is clear that it is preferable to arrange the ribs 103g in the range. Therefore, in FIGS. 3 and 4, two ribs 103g are arranged at one position located in the distal direction of the valve body 151 from the center of the valve seat 103e and at 90 degrees on both sides in the distal direction of the valve body 151. Has been established. The position of 90 degrees on both sides toward the distal end direction of the valve body 151 is located between the distal end side and the proximal end side of the valve body 151 of the valve seat 103e, but the rib 103g located at the distal end direction of the valve body 151 As a whole, the valve seat 103e or the distal end side of the valve body 151 in the peripheral portion including the valve seat 103e is reinforced from the base end side together with the ribs 103g located at 90 degrees on both sides.

  In the above embodiment, three ribs 103g are arranged. However, two or four or more ribs 103g may be arranged, and the intervals between the ribs 103g adjacent to each other in the circumferential direction may be equal intervals or unequal intervals. Either can be set.

Further, only one rib 103g may be provided. Based on the results shown in FIG. 13, one rib 103g is disposed in the range from the center of the valve seat 103e toward the distal end of the valve body up to about 45 degrees on the side with a large amount of collapse (left side in the figure). Seems to be preferred.
It should be noted that the arrangement positions and the number of the ribs described above are the same in the following embodiments.

Next, the case where the height of the rib 103g is set slightly lower than the seating surface (= valve plate surface) of the valve seat 103e will be described in the form shown in FIGS.
Also in this case, by reducing the elongated portion of the valve seat 103e provided with the rib 103g on the side higher than the top surface of the rib 103g, the slenderness ratio λ decreases and the buckling load increases. Thereby, even when a large compressive load is received due to an impact at the time of seating on the distal end side of the valve body 151, buckling can be effectively suppressed, and fatigue due to repeated compressive load can also be effectively suppressed (model diagram, FIG. 12). (See (C)). As a result, it is possible to suppress the deterioration of the compressor performance due to a decrease in sealing performance.

  On the other hand, by reducing the contact force by reducing the total seating area of the valve body 151 by the amount that the valve body 151 is not seated on the rib 103g, the noise suppression effect and the compressor efficiency maintenance effect can be further enhanced. .

  If the rib is also provided on the valve element base end side of the valve seat in the same way as the tip end side, the tip side seating part that receives a large compressive load is relatively durable against the base side seating part. Since it becomes weak, it becomes easy to damage from this weak part. In other words, in the present invention, the front-side seating portion that receives a large compressive load is reinforced from the base-side seating portion, and the durability of the entire valve seat is made uniform to effectively suppress crushing, buckling, and fatigue. It can be done.

  FIG. 5 shows the valve seat 103e as a setting in which the central axis of the outer peripheral surface is eccentric to the front end side of the valve body 151 with respect to the central axis of the valve hole 103a or 103b forming the inner peripheral surface thereof. An embodiment is shown in which the radial thickness of the seated portion is formed in a shape larger than the radial thickness of the seated portion on the base end side. In this embodiment as well, on the basis of the result of FIG. 13, it is decentered from the center of the valve seat toward the distal end of the valve body in the direction of about 45 degrees on the side with a large amount of crushing (left side in the figure).

  In the present embodiment, by increasing the seating area of the portion of the valve seat 103e where the front end side of the valve body 151 is seated, it is possible to reduce the surface pressure and suppress the collapse, and the cross-sectional area of the same portion increases and the seat is increased. Bending and fatigue can be suppressed, and as a result, deterioration of compressor performance can be suppressed.

  Further, the width of the valve seat 103e on which the base end side of the valve body 151 is seated can be narrowed to reduce the total seating area of the valve body 151 and the contact force can be reduced. It is possible to maintain good efficiency.

  FIG. 6 shows a plurality of ribs 103g extending in the radial direction from the peripheral wall of the valve seat 103e where the front end of the valve element 151 is seated and reaching the outer peripheral wall of the groove 103f, and the top surface of the rib 103g is It is formed in a shape having a plurality of parallel protrusions 103j along the direction.

As shown in the figure, the height of the protrusion 103j of the rib 103g is the same as the seating surface (= valve plate surface) of the valve seat.
With such a configuration, the valve body 151 is seated on each protrusion 103j of the rib 103g, so that the contact pressure can be reduced and the collapse can be suppressed.

Further, the rib 103g formed integrally with the valve seat 103e increases the cross-sectional area of this portion and decreases the slenderness ratio λ, thereby suppressing buckling and fatigue.
Thereby, deterioration of compressor performance can be controlled.

  In particular, in this embodiment, the top surface of the rib 103g is not a flat surface, and the protrusion 103j is provided, so that the increase in the seating area is limited to the minimum necessary size effective for suppressing crushing. A sufficiently large cross-sectional area can be secured to further increase the effect of suppressing buckling and fatigue.

FIG. 7 shows an embodiment in which the radial front ends of the ribs 103g extending in the radial direction from the peripheral wall of the portion on which the front end side of the valve body 151 of the valve seat 103e is seated do not reach the outer peripheral wall of the groove 103f.
Also in this case, the action of the rib 103g is the same as that of the embodiment of FIGS. 2 to 4 in the form in which the top surface of the rib 103g is the same height as the seating surface (= valve plate surface) of the valve seat, and in the slightly lower form. Similarly, in the form of the same height, crushing, buckling, and fatigue are suppressed, and in a slightly low form, deterioration of the compressor performance can be suppressed by suppressing buckling and fatigue, and by reducing the adhesion force. Noise can be suppressed and the efficiency of the compressor can be maintained well.

FIG. 8 shows an arrangement in which a tapered rib 103g that tapers from the bottom surface of the groove 103f of the valve seat 103e where the front end side of the valve body 151 is seated toward the top.
In the present embodiment, if the top end of the rib 103g is flush with the seating surface of the valve seat 103e, the compressive load from the valve body 151 is supported by the valve seat 103e and the rib 103g. Can be suppressed. In this case, as in the embodiment of FIG. 6, it is possible to suppress the collapse while limiting the increase in the seating area to the minimum necessary size effective for suppressing the collapse.

Further, by providing the rib 103g integrally with the valve seat 103e, the slenderness ratio λ of the portion where the rib 103g is disposed can be reduced to suppress buckling and fatigue.
Thereby, the performance degradation of a compressor can be suppressed.

  FIG. 9 shows the rib 103g that rises from the bottom surface of the groove 103f where the valve element 151 of the valve seat 103e is seated, separated from the valve seat 103e. The height of the rib 103g is the same as the seating surface (= valve plate surface) of the valve seat 103e.

  Even when the rib 103g is formed separately from the valve seat 103e as in the present embodiment, the valve body 151 can also be seated on the rib 103g to reduce the surface pressure of the valve seat 103e. Can be suppressed.

  On the other hand, since the rib 103g and the valve seat 103e are separated, the valve seat 103e itself is not directly reinforced, but the compression load of the valve seat 103e seated on the distal end side of the valve body 151 is reduced due to the reduction of the surface pressure. Therefore, the bending moment generated in the valve seat 103e is reduced, and as a result, buckling and fatigue can be suppressed.

Thereby, the performance degradation of a compressor can be suppressed.
In addition, since the total area of the valve element seating surface can be reduced by forming the partial rib 103g, noise can be suppressed and the compressor efficiency can be maintained well by reducing the adhesion.

  Although the embodiment described above is preferably applied to both the intake valve device and the discharge valve device, it is a matter of course that even when applied to only one of them, a certain effect can be obtained.

  In the above-described embodiment, the present invention is applied to a piston reciprocating type compressor. However, the present invention uses a reed valve that opens and closes to suck or discharge refrigerant, such as a scroll type. If it is a type compressor, it is applicable to all the compressors.

DESCRIPTION OF SYMBOLS 100 ... Compressor 101 ... Cylinder block 101a ... Cylinder bore 103 ... Valve plate 103a ... Valve hole (suction side)
103b ... Valve hole (discharge side)
103e ... Valve seat 103f ... Groove 103g ... Rib 104 ... Cylinder head 151 ... Valve body 151a ... Valve body 151b ... Discharge valve body 151A ... Base end portion 151B ... Tip portion

Claims (10)

A valve plate that is opened and closed to suck or discharge refrigerant and has a valve hole, and is formed on the outer peripheral edge of the valve hole of the valve plate so as to protrude into a boss shape with respect to a groove formed on the outer periphery of the valve plate. In the valve device of the compressor of the reed valve structure, the base end portion is connected to the valve plate and the valve plate is connected to and separated from the seating surface of the valve seat.
The shape of the valve seat or a peripheral portion including the valve seat is formed such that a portion corresponding to the distal end side of the valve body is reinforced with respect to a portion corresponding to the proximal end side of the valve body. Compressor valve device.   The valve device for a compressor according to claim 1, wherein one or more ribs extending radially outward from a portion of the valve seat corresponding to the front end side of the valve body are disposed.   The valve device for a compressor according to claim 2, wherein the rib is formed such that a height from a bottom of the groove is the same as or lower than a valve body seating surface of the valve seat. .   4. The valve device for a compressor according to claim 2, wherein the rib is formed so as to extend from an outer peripheral wall of the valve seat to an outer peripheral wall of the groove.   5. The compressor according to claim 2, wherein the rib is formed so as to extend from an outer peripheral wall of the valve seat to a midway from the outer peripheral wall of the groove to the outer peripheral wall of the groove. Valve device.   In the valve seat, the central axis of the outer circumferential circle is eccentric to the distal end side direction of the valve body with respect to the central axis of the valve hole forming the inner circumferential circle, and the radial thickness of the portion corresponding to the distal end side of the valve body 2. The valve device for a compressor according to claim 1, wherein the valve device is formed in a shape larger than a radial thickness of a portion corresponding to the base end side of the valve body.   The rib has a top surface in the height direction from the bottom of the groove, and a surface having a height lower than the seating surface of the valve seat and a surface having the same height are alternately arranged in the radial direction in parallel with the circumferential direction of the valve seat. The compressor valve device according to any one of claims 2 to 5, wherein the valve device is provided.   The rib corresponding to the seating surface of the said valve seat is arrange | positioned in the part corresponding to the said valve body front end side of the said groove | channel in parallel with the circumferential direction of this groove | channel. The valve device of the compressor described in 1.   2. The compressor according to claim 1, wherein a rib having a shape that tapers from the bottom of the groove toward the opening is disposed at a portion of the groove corresponding to the front end side of the valve body. Valve device.   One or more ribs are disposed within a central angle range of 90 degrees on both sides from the center of the valve hole toward the distal end of the valve body. The valve apparatus of the compressor as described in any one of Claims 9.